TWI465674B - Method for operation a once-through steam generator and forced-flow steam generator - Google Patents

Description

Operation method of operating direct current steam generator and forced direct steam generator

The invention relates to a method for operating a direct current steam generator with an evaporator heating surface, wherein a feed water mass flow Rating Transfer to feed water quality flow Adjustment device. The invention also relates to a forced direct current steam generator for carrying out the above method of operation.

In a direct current steam generator, the number of times of heating of a plurality of steam generator tubes that are used together to form the evaporator heating surface causes complete evaporation of the flowing medium in the steam generator tubes in a passage. Thus, the flowing medium (usually water) is typically conveyed prior to its evaporation to a preheater (also commonly referred to as an economizer) that is connected to the heating surface of the evaporator on the side of the flowing medium and preheated there.

The feed water mass flow in the evaporator heating surface is adjusted based on the operating state of the once-through steam generator and the actual steam generator power associated therewith. When the load changes, the flux in the evaporator should be changed as much as possible in synchronism with the amount of heat loading in the heating surface of the evaporator, otherwise the specificity of the flowing medium at the outlet of the heating surface of the evaporator cannot be reliably prevented (specific Enthalpy) deviates from a nominal value. This undesired deviation of the ratio causes the temperature of the fresh steam emitted by the steam generator to be unregulated and otherwise causes a high material load, which shortens the life of the steam generator.

In order to minimize the deviation of the specific enthalpy from the nominal value, and thus also to cause the undesired temperature fluctuations of the steam generator under all operating conditions (especially in the transient state or load switching) to be as small as possible, then Can be a so-called Predicted or foreseen design to adjust the flux of feedwater. Thus, the feed water rating required, particularly at the time of load switching, must be provided in accordance with actual or future desired operating conditions.

A direct current steam generator is known from EP 0 639 253, in which the feed water flux is adjusted by pre-calculating the required feed water quantity. Here, the heat flow balance of the evaporator heating surface is used as a reference for such a calculation method, wherein the feed water mass flow should, in particular, enter the inlet of the evaporator heating surface. The nominal value of the feed water mass flow is thus the heat flow that is actually transferred from the hot steam on the flowing medium to the heating surface of the evaporator, and the rating of the flowing medium in the evaporator heating surface for the desired fresh steam state.焓 Increase the value of the ratio between the two to preset.

However, it has actually been shown that measuring the feed water mass flow directly at the inlet of the evaporator heating surface is technically expensive and not reliably performed in every operating state. Instead, the feed water mass flow is measured at the inlet of the preheater and the feed water mass flow is included in the calculation of the feed water quantity, but the feed water mass flow is not in each case equal to the feed water quality at the inlet of the evaporator heating surface. flow.

In order to overcome the inaccuracy caused by the preset process when presetting the nominal value of the feedwater mass flow (especially when setting according to demand during load switching), another concept of adjusting the mass flow in a predictive manner is adopted. The feed water density at the inlet of the preheater is to be taken into account as one of the input values for the adjustment of the feed water flux, which is known, for example, from WO 2006/005708 A1.

The main input values of the above two concepts for adjusting the mass flow in a predictive manner are based on the rated value of the steam generator power, and thus are stored according to Correlation and in particular to consider previously obtained calibration measurements or reference measurements to calculate a characteristic value that flows in accordance with a particular rating specification. However, a prerequisite is that there must be system characteristics that are sufficiently stable and can be explicitly attributed to the heating power, which are typically present in the ignited steam generator. In addition, in other systems, for example, when the direct current steam generator is designed as a waste heat boiler to recover heat from the flue gas of a series of gas turbines, the above characteristics do not exist. Moreover, in such a system connected to a waste heat boiler, the heating power is not in the same range as the free parameter usable in a directly ignited boiler, since the operation of the gas turbine when connected to a waste heat boiler is generally regarded as The main criteria for the control of the entire equipment.

It is an object of the present invention to provide a method of operating a steam generator of the above type which, when less expensive, can also be used in the heating surface of the evaporator by the evaporator heating surface when the steam generator is operated as a waste heat boiler. The actual - or desired heat loading value is used to adjust the feed water mass flow. In addition, the present invention also provides a forced direct current steam generator that is particularly suitable for use in performing the above method.

In terms of method, the object of the invention is achieved by considering a temperature characteristic value representative of the actual temperature of the hot vapor at the inlet of the evaporator and a mass flow characteristic representative of the actual mass flow of the hot vapor. The heat flow delivered by the hot vapor to the flowing medium is measured in the case of a value.

The invention thus begins with the consideration that a sufficiently reliable predictive quality can also be used for a steam generator connected to a waste heat boiler. The flow adjustment should be widely adjustable based on the characteristics of the waste heat boiler. Therefore, in particular, it must be considered that in this case, unlike a ignited boiler, it can be sufficiently reliable to conclude that the heating power is not an appropriate parameter for the conclusion of the heat flow balance. Here, in particular, it should be considered that in an equivalent value to the waste heat boiler (ie the actual gas turbine power or related parameters), other parameters inside the gas turbine can still be added in order to enter the hot gas. It is not possible to make an acceptable inference of the ratio of the crucible to the vapour channel of the steam generator based on the above values. Other particularly suitable parameters should be used in determining the heat flow balance upon which the desired feed water flow is based. In addition, the hot vapor-temperature at the inlet in the evaporator and the mass flow of the hot vapor should be preset.

In the above manner, the required amount of water supply can be calculated in advance based on the heat flow balance of the evaporator, and the evaporator can also include the subsequent superheater heating surface when necessary. Therefore, in consideration of the hot vapor enthalpy at the outlet of the evaporator, the temperature characteristic value indicating the actual temperature of the hot vapor at the inlet of the evaporator can be used to find the heat at the inlet of the evaporator. A particularly reliable corresponding eigenvalue of the vapor enthalpy. The hot gas enthalpy can be calculated from the mass flow characteristic value used to represent the actual mass flow, and therefore the heat supplied to or transferred to the hot gas to the water can be determined particularly reliably as needed. The desired rated enthalpy increase value of the flowing medium in the heating surface of the evaporator can be determined by considering the predetermined rated enthalpy increase value, that is, in particular, the evaporator outlet can be determined. The nominal enthalpy of the flowing medium (which is measured when considering the desired fresh steam parameters) and the appropriate measured value at the inlet of the evaporator (eg, pressure) The difference between the actual enthalpy determined by the force and the temperature, wherein the other suitable ratings of the feed water mass flow can be calculated from the ratio of these values.

Preferably, a characteristic value, particularly representative of the actual situation, is considered as the temperature characteristic value and/or the mass flow characteristic value to appropriately describe the hot vapor entering the evaporator. These characteristic values can be determined as appropriate from the actual measurement data and can be used in particular to infer stored feature values. However, the heat flow balance can also be calculated particularly reliably and thus a particularly accurate pre-calculated feed water rating can be determined, in which case an actually measured measured value can be considered separately as a temperature characteristic value and/or a mass flow characteristic value. .

The heat flow delivered by the hot vapor to the flowing medium can be determined based on the heat flow balance, wherein the difference between the hot vapors between the evaporator inlet and the evaporator outlet can be taken as the primary input value. In this case, in terms of the calculation of particularly reliable eigenvalues, it is also necessary to consider that the energy content of the flue gas passing through the evaporator heating surface is reduced by the difference in enthalpy, which on the one hand causes a flow medium in the heating surface of the evaporator. The increase in enthalpy, but on the other hand, also causes energy inflow and/or outflow effects in the components of the evaporator, particularly in steam generating tubulars and other metal components. In order to determine particularly reliably the difference in enthalpy that is transmitted to the flow medium in the heating surface of the evaporator, the inflow and/or outflow of thermal energy in the metal substance can be considered as a correction value to appropriately correct the heat. The difference between the vapors.

In order to determine the difference between the hot vapor and the enthalpy of the hot vapor, the actual enthalpy of the hot vapor at the outlet of the evaporator must be considered, and the mass flow characteristic value of the actual mass flow of the hot vapor is considered. The pressure of the flowing medium at the inlet of the evaporator is used to determine the enthalpy. The mass flow characteristic value is preferably present in the form of a measured value or may be calculated directly by backtracking the stored correlation value or other characteristic value by other parameters. The mass flow characteristic value can thus advantageously be first calculated as the "pinch point" of the steam generator, i.e. calculated as the temperature difference between the outlet temperature of the flue gas and the boiling temperature of the flowing medium at the inlet of the evaporator. This temperature difference is appropriately added to the boiling temperature of the flowing medium determined by the pressure at the inlet of the evaporator, and thereby The enthalpy of the hot vapor at the outlet of the evaporator is determined.

The determination of the nominal enthalpy increase of the flowing medium in the heating surface of the evaporator is based on an appropriate measurement, for example, the pressure and temperature of the flowing medium at the inlet of the evaporator, based on the actual enthalpy that has been determined. Further, depending on the desired state of the vapor, for example, the steam parameter or vapor content at the outlet of the evaporator, the enthalpy of the flowing medium at the outlet of the evaporator is considered at the actual pressure of the flowing medium at the outlet of the heating surface of the evaporator. Preset a rating.

The direct current steam generator is operable in a so-called "Benson" control mode. In general, the Benson-controlled mode has overheating of the flowing medium at the exit of the evaporator heating surface. However, in this mode it is possible to allow an excess supply of the flow medium to the water reservoir after the heating surface of the evaporator and to transfer a portion of the unvaporized flow medium to the subsequent heating surface so that only thereafter The flowing medium completely evaporates in the heating surface. In this mode, in particular, the flow medium at the outlet of the evaporator is subjected to a nominal temperature adjustment as a desired steam parameter, which is higher than the flow medium. The saturation temperature is also higher than a predetermined temperature difference (for example, 35 ° C). In this mode of operation of the steam generator, the actual operating state of the spray cooler configured on the heating surface of the superheater connected to the heating surface of the evaporator may be considered, at which time the cooling demand of each of the spray coolers is transferred. Appropriate multiple supply surfaces to the system with feed water. Thus, the actual cooling demand in the spray cooler after attachment to the evaporator heating surface can be considered when presetting the nominal value of the flow medium at the outlet of the evaporator heating surface. Therefore, the nominal fresh steam temperature should in particular be achieved by adjusting the feed water flow as appropriate, so that the additional cooling requirements in each of the spray coolers can be kept particularly small. Conversely, when a too small fresh steam temperature has been determined, the enthalpy-rated value of the flowing medium at the outlet of the evaporator must be suitably increased to provide a feedwater mass flow with such altered rating. The amount of water supplied has been appropriately reduced.

Alternatively, the steam generator can be operated in a so-called "level control mode" in which the water level in the water reservoir connected to the heating surface of the evaporator is changed and readjusted. The water reservoir is prevented from being supplied excessively as much as possible. The water level in the water reservoir should be kept as far as possible within a predetermined range, wherein a full water level correction value can be considered in the advantageous configuration required for the nominal value of the feed water mass flow, which indicates the water reservoir The difference between the actual water level of the full water level and the associated rating.

In the case of a forced DC steam generator, the object of the invention is achieved in that a feedwater flux regulator associated with a device for adjusting the feed water mass flow is designed to preset the method according to the above method. The nominal value of the feed water mass flow. The forced DC steam generator is therefore advantageous In this way, a waste heat steam generator is formed which is applied with a waste steam discharged from the associated gas turbine plant on the hot steam side.

The advantages achievable with the invention are in particular: by appropriately considering the corresponding characteristic values of the actual temperature of the flue gas as it enters the hot gas channel and/or the actual mass flow of the flue gas, Or predetermining a feedwater mass flow rating that is particularly broadly oriented according to the desired demand, wherein even the steam generator is used as a waste heat boiler and therefore only slightly modified by the power or demand characteristic value of the equipment A particularly reliable and stable adjustment characteristic can also be achieved for the corresponding 焓 eigenvalues. Thus, in all possible operating states of the once-through steam generator, the feed water flux can be particularly reliably determined by the evaporator heating surface in accordance with the actual or desired heat loading of the steam heating surface. The adjustment is carried out, in particular in that the difference between the specific enthalpy of the flow medium at the outlet of the evaporator heating surface and the nominal value is kept particularly small.

Hereinafter, the embodiments of the present invention will be described in detail in accordance with the drawings.

The same elements in the various drawings are labeled with the same reference numerals.

The forced direct current steam generators 1, 1' of Figs. 1 and 2 each have a preheater 2 called an economizer for use with the feed water for the flowing medium. This preheater is located in a vapor flow device not shown in detail. A feed water pump is connected to the preheater 2 before the flow medium side and an evaporator heating surface 4 is connected to the preheater 2. On the output side, the evaporator heating surface 4 is connected on the flow medium side via a water reservoir 6 to a plurality of superheater heating surfaces 8, 10, 12 connected downstream, wherein the water reservoir 6 It is also possible to form a water separator or a water precipitation bottle. The superheater heating surface can be provided with spray coolers 14, 16 to adjust the steam temperature. The forced DC steam generators 1, 1' are respectively provided with a waste heat boiler or a waste heat steam generator, wherein each heating surface, in particular the preheater 2, the evaporator heating surface 4 and the superheater heating surface 8, 10, 12 are arranged In the hot gas passage on the side of the hot gas, waste steam discharged from the corresponding gas turbine is applied to the hot gas passage.

The forced direct current steam generator 1, 1 ' is designed to adjust the amount of water supplied. Here, the feed water pump 3 is connected to a throttle valve 22 controlled by the positioning motor 20 so that the feed water pump 3 can be in the direction of the preheater 2 by appropriate control of the throttle valve 22. The amount of water supplied in the medium is adjusted. In order to determine the actual characteristic value of the supplied water supply, a measuring device 24 is connected after the throttle valve 22 to measure the feed water-mass flow through the feed water line. . The positioning motor 20 is controlled by an adjustment element 28 which is applied with a feed water mass flow on the input side. Required rating transmitted via a data line 30 And a water quality flow is also applied The actual value measured by a measuring device 24. By forming a difference between the two signals, a re-directed demand can be transmitted to the adjuster 28 so that the positioning motor 20 can be controlled when the actual value and the rated value are different. A corresponding redirection of the throttle valve 22 is performed.

In order to measure the feed water mass flow in a predictive adjustment of the feed water mass flow or an adjustment method oriented according to future or actual demand Special rating required , the data line 30 on the input side must be used with a type to preset the feed water-mass flow Rating The water flux regulators 32, 32' are connected. The data line 30 measures the feed water mass flow based on the heat flow balance in the evaporator heating surface 4. Rating , the water quality flow Rating It is preset based on the heat flow (a value) actually transferred from the hot vapor to the flowing medium in the evaporator heating surface 4 and the desired fresh steam state of the flowing medium in the evaporator heating surface. The rated 焓 increase value (another value) is preset by the ratio between the two values. For the forced DC steam generator 1,1' constructed as a waste heat boiler, this concept is used to prepare the nominal value of the feed water mass flow based on the heat balance itself, which is shown in Figures 1 and 2. In particular, the embodiment is achieved in that the heat flow from the hot vapor to the flowing medium takes into account a temperature characteristic value indicative of the actual temperature of the hot vapor at the inlet of the evaporator and a heat vapour. The mass flow characteristic value of the actual mass flow is obtained.

Here, the feedwater flux regulator 32 has a dividing element 34, an appropriate characteristic value (as a molecule) of the heat flow actually transferred from the hot vapor to the flowing medium in the evaporator heating surface 4, and An appropriate predetermined characteristic value (as a denominator) of the desired nominal value of the flow medium in the evaporative vapor heating surface 4 is transmitted to the dividing element 34 in the desired fresh steam state. On the counter side, the dividing element 34 is connected to a function module 36 on the input side, and the function module 36 issues the temperature characteristic value according to the transmitted actual temperature of the hot vapor on the inlet side of the evaporator. The value of the hot vapor is taken to the evaporator inlet as an output value. In this embodiment, a measurement value indicating the actual temperature of the hot vapor at the inlet side of the evaporator is to be provided as the temperature characteristic value. The characteristic value indicating the enthalpy of the hot vapor at the inlet side of the evaporator is sent to a subtraction element 38, in which the subtraction element 38 is The characteristic value is subtracted from a characteristic value corresponding to the enthalpy of the vapor at the outlet of the evaporator provided by a functional module 40.

In order to determine the enthalpy of the hot vapor at the outlet of the evaporator, a sum of the two temperature values is formed by an addition element 42 on the input side of the functional module 40. Thus, on the one hand, the saturation temperature of the flow medium measured via the functional element 44 at the evaporator inlet depending on the pressure of the flowing medium is considered, wherein the functional element 44 is connected to a pressure sensor 46 on the input side. On the other hand, a so-called "pinch point" (the definition of which has been described above) is considered by a functional element 48, and a mass flow characteristic value for indicating the actual mass flow of the hot vapor is transmitted to The functional element 48. By the above two temperature values added by the adding element 42, the function module 40 can be used to provide the hot gas at the outlet of the evaporator, and the appropriate form, figure or pattern can be traced back when necessary. analog. The subtracting element 38 provides a difference or balance of the enthalpy of the hot vapor on the output side, i.e., the difference between the hot vapor enthalpy at the evaporator inlet and the hot vapor enthalpy at the evaporator outlet.

The difference in such enthalpy continues to be passed to multiplier 52, which also transmits the mass flow eigenvalues to the multiplier 52 as well. The multiplier 52 thus provides a characteristic value of the thermal power emitted by the flue gas to the evaporator heating surface 4 on the output side.

In order to determine the heat flow actually delivered to the flowing medium based on the thermal power emitted by the hot gas, the heat loading and/or heat in the components of the evaporator heating surface 4, in particular the metal species, must first be applied. The effect is corrected. Here, the above characteristic value of the thermal power emitted by the hot vapor is first transmitted to the subtracting element 54 where a correction value indicating the heat loading or heat emitting value in the evaporator member is subtracted. This correction value is provided by functional element 56. another The output value of a functional module 58 is applied to the functional component 56 on the input side, at which point the average temperature of the metal species of the evaporator heating surface 4 must be measured. Thus, the functional element 58 is connected on the input side to a pressure indicator 60 disposed in the water reservoir 6, such that the functional element 58 can determine each metal based on the pressure of the flowing medium in the water reservoir 6. The average temperature of the substance.

The subtracting element 54 thus produces on the output side a characteristic value obtained by reducing the thermal power stored in the metal of the evaporator heating surface 4 by the thermal power emitted to the hot vapor, which is thus indicated to The thermal power value of the flowing medium.

This characteristic value is used as a numerator in the dividing element 34, where it is divided by a denominator which is a rating of the flowing medium in the evaporator heating surface 4 for the desired fresh steam state. Increasing the value to form the feedwater mass flow from such a division relationship Rating . In order to provide the denominator to the water vapor side or the flow medium side, the dividing element 34 has to be connected to a subtracting element 70 on the input side. A characteristic value provided by functional element 72 (which is used to indicate the desired rating of the flowing medium at the outlet of the evaporator) is applied to the subtracting element 70 on the input side. Furthermore, a characteristic value or an actual value provided by the functional element 74 (which is used to represent the actual enthalpy of the flowing medium at the inlet of the evaporator) is applied to the subtracting element 70 on the input side, the actual value being subtracted from the subtracting element 70. The characteristic value corresponding to the rating of the flowing medium at the outlet of the evaporator is removed. The functional element 74 is thus coupled to the pressure sensor 46 and the temperature sensor 76 on the input side to form the aforementioned characteristic value corresponding to the actual volume of the flowing medium at the evaporator inlet. By the formation of the difference in the subtracting element 70, the enthalpy increase value applied to the flowing medium in the evaporator heating surface 4 in accordance with the desired fresh steam state can be determined, which is used as the denominator in the dividing element 34. .

The difference between the forced DC steam generators 1, 1' in Figures 1 and 2 is the formation of the water supply flux regulators 32, 32', especially at the evaporator outlet. This difference is the function module 72 provided on the input side. The forced DC steam generator 1 of Fig. 1 is therefore used in the operation of the so-called "level control mode" in which the water level in the water reservoir 6 has to be adjusted, and the steam is only continuously transferred to the evaporator heating surface 4 The superheater heats the faces 8, 10, 12, and the water that is delivered is still deposited in the water reservoir 6 on the evaporator output side. In this mode of operation, the functional module 72 is applied on the input side on the one hand to provide a measurement of the pressure in the water reservoir 6 provided by the pressure sensor 60. On the other hand, a parameter (e.g., desired vapor content) indicative of the desired fresh steam state at the outlet side of the evaporator is communicated to the functional module 72 via the associated input 78. Then, the nominal value corresponding to the enthalpy of the flowing medium at the outlet of the evaporator is formed in the functional module 72 by the parameters having the above-described pressure characteristic values.

In the configuration of Fig. 1, the dividing element 34 supplies the rated value of the feed water mass flow on the output side in accordance with the above-described division relationship, which is set and determined in accordance with the above-described heat balance. This rating then corrects a correction value in a summing element 80 connected to the rear which in turn causes a desired change in the feed water flux in the level state in the water reservoir 6. Here, the level state in the water reservoir 6 is measured by a full state sensor 82. The actual value of the full state subtracts the stored nominal value corresponding to the full state of the water reservoir 6 in a subtraction element 84 or subtracts the nominal value that can be preset in another manner. Depending on the determined difference between the actual state of the full state and the associated nominal value in the water reservoir 6, an effective feedwater mass flow value can be measured in the subsequent positioning element 86, this value being applied to The water reservoir 6 corrects the full state of the water reservoir 6. The correction value is added to the nominal value measured by the heat flow balance of the feed water mass flow in the addition element 80 to emit a value composed of two components as the nominal value of the feed water mass flow. .

Similarly, the forced DC steam generator 1' of Fig. 2 is designed to operate in a so-called "Banson-control mode" in which the excess supply of the water reservoir 6 for the water separator and the complete evaporation of the flowing medium are only This is only possible in the subsequent superheater heating faces 8, 10, 12. In this mode of operation, the functional element 72 is likewise applied on the input side with the actual value measured by the pressure sensor 60 corresponding to the pressure in the water reservoir 6. In addition, before the input side is connected to the function module 72, the function module 90 measures the water reservoir according to the actual pressure in the water reservoir 6 measured by the pressure sensor 60. 6 The appropriate rating of the temperature of the flowing medium. For example, in the case of the device operating in "Banson-Control Mode", a temperature value can be stored as a temperature rating, which corresponds to a measured pressure including a preset minimum overheat of, for example, 35 °C. The saturation temperature of the flowing medium. The function module 72 determines the enthalpy of the flowing medium at the outlet of the evaporator from the rated value of the temperature when considering the actual pressure value. Rating.

In the embodiment of Fig. 2, the nominal value provided by functional unit 72 is then changed in the subsequent addition element 92 to be another correction value. Another correction value provided by the functional unit 94 is trimmed (tri The way of function takes into account the difference between the actually determined fresh steam temperature and the desired fresh steam temperature. Such a difference is of particular concern for the following reasons: the fresh steam temperature of the spray coolers 14, 16 is too high to have a cooling requirement and therefore the spray coolers 14, 16 need to be applied. To cool the medium. If the mass flow applied to the spray coolers 14, 16 has been determined, the functional module 94 is designed to transfer the cooling requirements of the spray coolers 14, 16 back and forth to a higher feed water supply. Area. When the cooling requirements in each of the spray coolers 14, 16 have been determined, the desired enthalpy of the flowing medium at the evaporator outlet in the functional module 94 must be reduced to minimize cooling requirements. Otherwise, when a too small fresh steam temperature has been determined, the correction value provided by the functional module 94 and its addition in the summing element 92 can increase the crucible rating.

For safety, the feedwater flux regulator 32' of the forced DC steam generator 1' of Fig. 2 further includes an adjustment loop directly connected to the rear, wherein the measured value in the water reservoir 6 is in the functional module 100. The actual value of the enthalpy of the flowing medium at the outlet of the evaporator is measured and compared to the desired enthalpy (i.e., the nominal enthalpy) in the subtraction module 102. By the formation of the difference in the subtraction module 102, a nominal actual deviation value can be determined which is provided by the dividing element 34 superimposed on the feedwater mass flow in the summing element 106 via a subsequent regulator 104. Rating. this The overlay must be appropriately delayed in time and attenuated so that adjustments are made only when needed, i.e., when the adjustment offset is too rough.

1,1'‧‧‧Forced DC steam generator

2‧‧‧Preheater (energy saver)

3‧‧‧Water pump

4‧‧‧ evaporator heating surface

6‧‧‧Water storage

8,10,12‧‧‧Superheater heating surface

14,16‧‧‧Injection cooler

20‧‧‧ Positioning motor

22‧‧‧ throttle valve

24‧‧‧Measurement device

28‧‧‧Adjusting components/regulators

30‧‧‧Information line

32,32’‧‧‧Water supply flux regulator

34‧‧‧Division components

36‧‧‧Function module

38‧‧‧Subtraction components

40‧‧‧ function module

42‧‧‧Adding components

44‧‧‧Functional components

46‧‧‧pressure sensor

48, 50‧‧‧ functional components

52‧‧‧Multiplier

54‧‧‧Subtraction components

56,58‧‧‧ functional components

60‧‧‧ Pressure indicator / pressure sensor

70‧‧‧Subtraction component

72‧‧‧Functional components/modules

74‧‧‧ function module

76‧‧‧Temperature Sensor

78‧‧‧ input

80‧‧‧Adding components

82‧‧‧ Full state sensor

84‧‧‧Subtraction components

86‧‧‧ Positioning components

90‧‧‧ function module

92‧‧‧Adding components

94‧‧‧ function module

100‧‧‧ functional modules

102‧‧‧Subtraction module

104‧‧‧ adjuster

106‧‧‧Adding components

‧‧‧Water quality flow

‧‧‧Rated

Figures 1 and 2 show the forced DC steam generator with feedwater flux regulator, respectively.

2‧‧‧Preheater (energy saver)

3‧‧‧Water pump

4‧‧‧ evaporator heating surface

6‧‧‧Water storage

8,10,12‧‧‧Superheater heating surface

14,16‧‧‧Injection cooler

20‧‧‧ Positioning motor

22‧‧‧ throttle valve

24‧‧‧Measurement device

28‧‧‧Adjusting components/regulators

30‧‧‧Information line

32‧‧‧Water supply flux regulator

34‧‧‧Division components

36‧‧‧Function module

38‧‧‧Subtraction components

40‧‧‧ function module

42‧‧‧Adding components

44‧‧‧Functional components

46‧‧‧pressure sensor

48, 50‧‧‧ functional components

52‧‧‧Multiplier

54‧‧‧Subtraction components

56,58‧‧‧ functional components

60‧‧‧ Pressure indicator / pressure sensor

70‧‧‧Subtraction component

72‧‧‧Functional components/-modules

74‧‧‧ function module

76‧‧‧Temperature Sensor

78‧‧‧ input

80‧‧‧Adding components

82‧‧‧ Full state sensor

84‧‧‧Subtraction components

86‧‧‧ Positioning components

Claims (11)

A method of operating a direct current steam generator having an evaporator heating surface (4) in which a feed water mass flow ( Rating) Transfer to adjust this feedwater mass flow ( a device for the feed water mass flow from a heat flow value actually transferred from the hot vapor to the flow medium in the evaporator heating surface (4) and a flow medium in the evaporator heating surface (4) for the desired The ratio of the fresh steam state to the preset nominal enthalpy increase value is preset, wherein the heat flow value transmitted by the hot vapor to the flowing medium is in consideration of an actual temperature for indicating the hot vapor at the inlet of the evaporator. The temperature characteristic value and a mass flow characteristic value used to represent the actual mass flow of the hot vapor are measured. For example, in the method of operation of claim 1, wherein an actual measured value is to be considered separately for the temperature characteristic value and/or the mass flow characteristic value. The method of operation of claim 1 or 2, wherein the heat flow value transmitted from the hot vapor to the flowing medium is determined based on a difference in thermal vapor between the inlet of the evaporator and the outlet of the evaporator. The method of operation of claim 3, wherein the difference in the value of the hot vapor is corrected by a correction value indicating the value of the heat in or out of the evaporator member to obtain the flow from the hot vapor to the flow. The value of the heat flow in the medium. The method of operation of claim 3, wherein the actual enthalpy of the hot vapor at the outlet of the evaporator is measured in consideration of the mass flow characteristic value in accordance with the pressure of the flowing medium at the inlet of the evaporator. For example, the operation method of the first application of the patent scope, wherein the evaporator heating surface The rated enthalpy increase of the flowing medium in (4) is preset when considering the actual pressure of the flowing medium at the outlet of the evaporator heating surface (4). The method of operation of claim 6, wherein the nozzle connected to the heating surface (4) of the evaporator must be considered when presetting the rating of the flowing medium at the outlet of the evaporator heating surface (4). The actual cooling requirements in the inlet cooler (14, 16). For example, the method of operation of claim 1 shall be directed to the feed water mass flow ( Rating) Consider a full state correction value which represents the difference between the actual state of the full state in the water reservoir (6) connected to the evaporator heating surface (4) and the associated nominal value. For example, the method of operation of claim 1 shall be directed to the feed water mass flow ( Rating) Considering a 焓 correction value, which represents the difference between the actual state of the enthalpy at the exit of the evaporator heating surface (4) and the associated rating. A forced DC steam generator (1, 1') having an evaporator heating surface (4) and a feed water mass flow ( a device for adjustment, which is based on the mass flow of the feed water ( Rating) And being guided, characterized in that an associated feedwater flux adjuster (32, 32') is designed to preset the rating according to the method of operation of any one of claims 1 to 9 ( ). A forced direct current steam generator (1, 1') as claimed in claim 10, wherein the exhaust steam discharged from an associated gas turbine plant is applied to the hot steam side.